US7255289B2 - Fuel injector for an internal-combustion engine - Google Patents

Fuel injector for an internal-combustion engine Download PDF

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Publication number
US7255289B2
US7255289B2 US11/112,786 US11278605A US7255289B2 US 7255289 B2 US7255289 B2 US 7255289B2 US 11278605 A US11278605 A US 11278605A US 7255289 B2 US7255289 B2 US 7255289B2
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Prior art keywords
actuator
open
close element
terminal portion
injector
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US11/112,786
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US20060102755A1 (en
Inventor
Mario Ricco
Sisto Luigi De Matthaeis
Adriano Gorgoglione
Marco Petrachi
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Centro Ricerche Fiat SCpA
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Centro Ricerche Fiat SCpA
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Assigned to C.R.F. SOCIETA CONSORTILE PER AZIONI reassignment C.R.F. SOCIETA CONSORTILE PER AZIONI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DE MATTHAEIS, SISTO LUIGI, GORGOGLIONE, ADRIANO, PETRACHI, MARCO, RICCO, MARIO
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the present invention relates to a fuel injector for an internal-combustion engine.
  • fuel injectors comprise an outer shell, a terminal portion of which is designed to be housed in a fixed position in the cylinder head and is provided with a nozzle. Opening and closing of the nozzle are performed by a pin that moves along an axis under the control of an actuator, for example of an electromagnetic type.
  • the shell houses a servo valve, set between the actuator and the movable pin and comprising a control chamber, which has a calibrated inlet channel communicating with the fuel supply, and a calibrated outlet channel, opening and closing of which is performed by an open/close element operated by the actuator.
  • injectors in which the servo valve and the actuator are arranged in the terminal portion of the injector in the proximity of the nozzle.
  • the servo valve has a substantially cylindrical open/close element, which slides in an axial seat, fixed with respect to the shell, whilst the outlet channel of the control chamber gives out into an annular groove or chamber made radially between the side surfaces of the open/close element and of the axial seat.
  • the axial balancing of the actions of pressure acting on the open/close element of the servo valve is, in practice, not optimal, for example on account of the machining tolerances, the wear, and the deformations due to thermal stresses deriving from the parts of the engine in contact with the injector and/or to mechanical stresses.
  • the resulting unbalancing is the greater the smaller are the dimensions of the servo valve, in so far as the dimensional variations due to the aforesaid causes are percentagewise more important on small dimensions.
  • the purpose of the present invention is to provide a fuel injector for an internal-combustion engine which will enable the drawbacks described above to be overcome in a simple and economically advantageous way, improving known injectors with balanced servo valves of the type described above.
  • a fuel injector for an internal-combustion engine comprising:
  • FIG. 1 shows, in cross-sectional view and with parts removed for reasons of clarity, a preferred embodiment of a fuel injector for an internal-combustion engine according to the present invention
  • FIG. 2 is similar to FIG. 1 and shows, at an enlarged scale, a variant of a detail of the injector of FIG. 1 .
  • the reference number 1 designates, as a whole, a fuel injector (partially shown) for an internal-combustion engine, in particular for a diesel engine (not shown).
  • the injector 1 comprises an outer structure or shell 2 , which extends along a longitudinal axis 3 and comprises two opposite axial terminal portions 4 and 5 .
  • the portion 4 generally extends, in use, outside the engine, carries an axial connector 6 for electrical supply (visible in the solution of FIG. 2 ), has a side inlet 7 designed to be connected to a system (not shown) for supply of fuel, and defines an internal cavity 8 .
  • the portion 5 instead, has, in a direction transverse to the axis 3 , an external dimension D 1 smaller than the dimension D 2 of the portion 4 , is generally housed, in use, in a fixed position in the cylinder head, and ends with an atomizer.
  • the atomizer comprises: a nozzle 9 , which is designed to inject the fuel into a corresponding cylinder of the engine and communicates with the inlet 7 through a pipe 10 made in the portion 5 in an eccentric position with respect to the axis 3 ; and a pin 11 , which is axially movable for opening/closing the nozzle 9 under the control of a rod 13 (partially shown).
  • the rod 13 engages a seat 14 (partially shown) made in the portion 5 along the axis 3 and giving out into the cavity 8 , is coaxial to the pin 11 , and is axially slidable in the seat 14 under the control of a servo valve 15 actuated by an electrically controlled actuator 16 .
  • the servo valve 15 is set in an intermediate axial position between the rod 13 and the actuator 16 .
  • the actuator 16 and the servo valve 15 are both housed in the portion 4 .
  • the actuator 16 is coaxial to the rod 13 and comprises: an electromagnet 17 , electrically supplied through the connector 6 ; an anchor 18 , which has a generally sectored shape and is axially movable under the action of the electromagnet 17 ; and a pre-loaded spring 21 surrounded by the electromagnet 17 and exerting an action of thrust on the anchor 18 in a direction opposite to the attraction exerted by the electromagnet 17 itself.
  • the servo valve 15 instead, comprises a control chamber 23 , which is defined by one end of the rod 13 and by a body 24 shaped like a beaker turned upside down that is fixed with respect to the shell 2 , has a channel 25 for outlet of the fuel, the shape and arrangement of which is not described in detail, and communicates with the inlet 7 through a passage 26 partly made through the body 24 and partly through the shell 2 .
  • the servo valve 15 further comprises a seat 27 made along the axis 3 through a body 28 , which is housed in the cavity 8 in a fixed position with respect to the shell 2 and is coupled to a disk 29 so that it axially bears thereupon and is in a fixed reference angular position, said disk 29 being set between the bodies 24 , 28 .
  • the seat 27 is engaged by an open/close element 32 , which is defined by a substantially cylindrical axial pin, is fixedly connected to the anchor 18 , and is axially slidable in the seat 27 , substantially in a fluid-tight way, under the action of the electromagnet 17 for opening/closing the outlet of the channel 25 .
  • an open/close element 32 which is defined by a substantially cylindrical axial pin, is fixedly connected to the anchor 18 , and is axially slidable in the seat 27 , substantially in a fluid-tight way, under the action of the electromagnet 17 for opening/closing the outlet of the channel 25 .
  • the channel 25 is made in the bodies 24 , 28 and in the disk 29 and gives out into an annular chamber 34 made, radially, between the internal side surface of the seat 27 and the external side surface of the open/close element 32 , so as to render substantially zero the resultant of the axial actions of pressure on the open/close element 32 itself.
  • the chamber 34 is dug into the external side surface of the open/close element 32 .
  • the outlet of the channel 25 is opened, in use, by the displacement of the open/close element 32 into a raised opening position, following upon excitation of the electromagnet 17 .
  • the channel 25 and, hence, the chamber 23 are set in communication with a discharge pipe, so that the pressure in the chamber 23 decreases, causing raising of the rod 13 and thus opening of the nozzle 9 .
  • the elastic action of the spring 21 causes lowering of the open/close element 32 into the closing position, with a consequent increase in the pressure in the chamber 23 and, hence, closing of the nozzle 9 .
  • the seat 27 axially ends with a blind portion 38 , which is defined by the disk 29 and by the open/close element 32 , and communicates with the aforesaid discharge pipe via a through hole 39 , which is made through the open/close element 32 along the axis 3 and is distinct from the chamber 34 .
  • the blind portion 38 is defined axially by the open/close element 32 , on one side, and by an applied plate, on the other side. Said plate closes an axial through opening made in the disk 29 .
  • FIG. 2 shows a variant of the injector 1 , the constituent parts of which are designated, where possible, by the same reference numbers as the ones used in FIG. 1 .
  • the open/close element 32 forms part of a pin 40 distinct from the anchor 18 .
  • the anchor 18 has a cylindrical axial hole 42
  • the pin 40 comprises an intermediate portion 43 , which engages the hole 42 , and a terminal portion 44 opposite to the open/close element 32 .
  • the portion 44 is housed in the electromagnet 17 in an axially slidable way, has an end face 45 set bearing axially upon the spring 21 , and is connected to the portion 43 by means of a shoulder 46 set bearing upon a shoulder 47 of the anchor 18 .
  • the coupling between the shoulders 46 , 47 is defined by a coupling between a spherical surface and a conical surface, so as to obtain an articulated joint.
  • the shoulder 47 pushes the portion 44 axially so as to raise the open/close element 32 and hence cause opening of the nozzle 9 .
  • the elastic action of the spring 21 causes lowering of the pin 40 until the chamber 34 is closed, so as to bring about closing of the nozzle 9 , whilst the shoulder 46 pushes the anchor 18 axially in a direction opposite to the electromagnet 17 .
  • the servo valve 15 of a balanced type has available a relatively large space in a direction transverse to the axis 3 in the portion 4 , as compared to that available in the portion 5 , in so far as, as has been described, the portion 4 has a diameter greater than the portion 5 .
  • the inlet 7 since the inlet 7 is made laterally in an intermediate axial position between the seat 27 and the nozzle 9 , it enables prevention of passage of fuel at a relatively high pressure in the proximity of the servo valve 15 , contributing to increasing the space available for the servo valve 15 and at the same time to improving the hydraulic lay-out inside the electroinjector 1 , both from the standpoint of simplification of the construction of the internal holes and from the standpoint of optimization of the permeability of the holes and of the points of crossing-over thereof.
  • the pipe 10 in fact, extends alongside the seat 14 , and not alongside the cavity 8 in which the servo valve 15 is partially housed.
  • the servo valve 15 since it is possible for the servo valve 15 to have larger dimensions (in particular the diameters of coupling and of seal may be greater) given the same precision required, the fabrication and machining of its components are simpler as compared to known solutions in which the servo valve of a balanced type described is housed in the terminal part near the nozzle, which is inserted in the engine.
  • the dimensions of the diameters of the coupled surfaces and of the diameters of sealing may be similar to those of the atomizers, enabling use for their fabrication of the same process technologies as those used for the atomizers, which are by now consolidated and well tested.
  • the open/close element 32 (which only theoretically is perfectly balanced) it is possible to tolerate, and compensate, in use, even the imbalance of actions along the axis 3 , due for example to machining tolerances, wear, and deformations due to thermal and/or mechanical stresses.
  • the diameter of sealing of the pipes of the servo valve 15 may be greater, so that, given the same outflow necessary for correct operation of the injector 1 , it is possible to envisage, for the open/close element 32 , strokes equal to approximately one half those of known solutions of a balanced type, with consequent further benefits in the dynamic behaviour of the injector 1 .
  • the relatively small values of the stroke of the open/close element 32 simplify considerably the achievement of the end-of-travel of the open/close element 32 itself, in so far as it is possible to obtain it by causing the anchor 18 to hit axially against the front wall of the electromagnet 17 (with or without interposition of intermediate means) thanks to the reduced momentum to be absorbed. Furthermore, if the surfaces that come into contact during impact have an area greater than 0.5 square centimetres, an effect of damping of the anchor 18 is obtained, which further improves the dynamic behaviour of the injector 1 .
  • the reduced strokes of the open/close element 32 also reduce the effects of wear of the components coming into contact, with a corresponding smaller variation in time of the stroke of the open/close element 32 .
  • said stroke is halved with respect to known solutions of a balanced type described above, after approximately two hours of normal operation of the injector 1 , the variation of the stroke itself due to wear is approximately eight times smaller.
  • the architecture forming the subject of the present patent further enables use of the well-validated “two-pin” architecture for the electroinjector 1 , i.e., it makes it possible to keep the two components, the rod 13 and the pin 11 , physically and functionally distinct.
  • the rod 13 and the pin 11 can have different diameters with respect to one another and such as to determine an appropriate difference in area, which will generate a force capable of improving the mechanisms of opening and closing of the nozzle 9 .
  • the hole 39 is relatively easy to make and does not entail any further machining operations either on the shell 2 or on the servo valve 15 in order to set the portion 38 of the seat 27 in discharge.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
US11/112,786 2004-11-12 2005-04-21 Fuel injector for an internal-combustion engine Active 2026-02-09 US7255289B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP04425842A EP1657435B8 (de) 2004-11-12 2004-11-12 Einspritzventil für Brennkraftmaschine
EP04425842.4 2004-11-12

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US20060102755A1 US20060102755A1 (en) 2006-05-18
US7255289B2 true US7255289B2 (en) 2007-08-14

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US11/112,786 Active 2026-02-09 US7255289B2 (en) 2004-11-12 2005-04-21 Fuel injector for an internal-combustion engine

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US (1) US7255289B2 (de)
EP (1) EP1657435B8 (de)
JP (1) JP4404801B2 (de)
AT (1) ATE355458T1 (de)
DE (1) DE602004005052T2 (de)
ES (1) ES2280932T3 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100294241A1 (en) * 2008-01-22 2010-11-25 Nadja Eisenmenger Fuel injector the control valve element of which has a support region

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007001554A1 (de) * 2007-01-10 2008-07-17 Robert Bosch Gmbh Kraftstoffinjektor
DE102007038394A1 (de) * 2007-08-14 2009-02-19 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor
DE102012218593A1 (de) * 2012-10-12 2014-04-17 Continental Automotive Gmbh Ventil für eine Pumpe
GB201505094D0 (en) * 2015-03-26 2015-05-06 Delphi International Operations Luxembourg S.�.R.L. Control valve arrangement
WO2020039955A1 (ja) * 2018-08-24 2020-02-27 日立オートモティブシステムズ株式会社 燃料噴射弁

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408718A (en) * 1981-09-25 1983-10-11 General Motors Corporation Electromagnetic unit fuel injector
US4527737A (en) * 1983-09-09 1985-07-09 General Motors Corporation Electromagnetic unit fuel injector with differential valve
US4572433A (en) * 1984-08-20 1986-02-25 General Motors Corporation Electromagnetic unit fuel injector
EP0823549A2 (de) 1996-08-06 1998-02-11 Lucas Industries Public Limited Company Einspritzventil
EP0916843A1 (de) 1997-11-18 1999-05-19 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Einstellbares Dosierventil für Kraftstoffeinspritzventil einer Brennkraftmaschine
GB2336628A (en) 1998-04-24 1999-10-27 Lucas Ind Plc A fuel injector, for an I.C. engine, having a three way two position needle control valve
GB2350662A (en) 1999-06-03 2000-12-06 Lucas Ind Plc Valve for a fuel injector
US6425532B1 (en) * 2000-01-12 2002-07-30 Woodward Governor Company Gaseous fuel injector having spring loaded metal seal
WO2003004861A1 (de) 2001-07-04 2003-01-16 Robert Bosch Gmbh Kraftstoffinjektor mit kraftausgeglichenem steuerventil
EP1382837A2 (de) 2002-07-15 2004-01-21 Caterpillar Inc. Brennstoffeinspritzventil mit direktgesteuerter Düse und Brennstoffeinspritzsystem mit einer solchen Düse
US6889659B2 (en) * 2003-04-02 2005-05-10 Robert Bosch Gmbh Fuel injector with pressure booster and servo valve with optimized control quantity

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO20010814A1 (it) * 2001-08-14 2003-02-14 Fiat Ricerche Iniettore di combustibile per un motore endotermico e relativo metododi fabbricazione.

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408718A (en) * 1981-09-25 1983-10-11 General Motors Corporation Electromagnetic unit fuel injector
US4527737A (en) * 1983-09-09 1985-07-09 General Motors Corporation Electromagnetic unit fuel injector with differential valve
US4572433A (en) * 1984-08-20 1986-02-25 General Motors Corporation Electromagnetic unit fuel injector
EP0823549A2 (de) 1996-08-06 1998-02-11 Lucas Industries Public Limited Company Einspritzventil
EP0916843A1 (de) 1997-11-18 1999-05-19 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Einstellbares Dosierventil für Kraftstoffeinspritzventil einer Brennkraftmaschine
GB2336628A (en) 1998-04-24 1999-10-27 Lucas Ind Plc A fuel injector, for an I.C. engine, having a three way two position needle control valve
GB2350662A (en) 1999-06-03 2000-12-06 Lucas Ind Plc Valve for a fuel injector
US6425532B1 (en) * 2000-01-12 2002-07-30 Woodward Governor Company Gaseous fuel injector having spring loaded metal seal
WO2003004861A1 (de) 2001-07-04 2003-01-16 Robert Bosch Gmbh Kraftstoffinjektor mit kraftausgeglichenem steuerventil
EP1382837A2 (de) 2002-07-15 2004-01-21 Caterpillar Inc. Brennstoffeinspritzventil mit direktgesteuerter Düse und Brennstoffeinspritzsystem mit einer solchen Düse
US6889659B2 (en) * 2003-04-02 2005-05-10 Robert Bosch Gmbh Fuel injector with pressure booster and servo valve with optimized control quantity

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
European Search Report EP 04 42 5842 Dated Feb. 28, 2005.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100294241A1 (en) * 2008-01-22 2010-11-25 Nadja Eisenmenger Fuel injector the control valve element of which has a support region
US8671912B2 (en) * 2008-01-22 2014-03-18 Robert Bosch Gmbh Fuel injector the control valve element of which has a support region

Also Published As

Publication number Publication date
JP2006138311A (ja) 2006-06-01
EP1657435B1 (de) 2007-02-28
DE602004005052T2 (de) 2007-11-15
DE602004005052D1 (de) 2007-04-12
EP1657435B8 (de) 2007-05-09
ATE355458T1 (de) 2006-03-15
ES2280932T3 (es) 2007-09-16
EP1657435A1 (de) 2006-05-17
JP4404801B2 (ja) 2010-01-27
US20060102755A1 (en) 2006-05-18

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